US3276102A - Adjustable crown roll - Google Patents

Adjustable crown roll Download PDF

Info

Publication number
US3276102A
US3276102A US339998A US33999864A US3276102A US 3276102 A US3276102 A US 3276102A US 339998 A US339998 A US 339998A US 33999864 A US33999864 A US 33999864A US 3276102 A US3276102 A US 3276102A
Authority
US
United States
Prior art keywords
roll
shell
roll shell
nip
shoe
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US339998A
Other languages
English (en)
Inventor
Edgar J Justus
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Beloit Corp
Original Assignee
Beloit Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to FR61716A priority Critical patent/FR95913E/fr
Application filed by Beloit Corp filed Critical Beloit Corp
Priority to US339998A priority patent/US3276102A/en
Priority to FR992308A priority patent/FR1412267A/fr
Priority to ES0305227A priority patent/ES305227A1/es
Priority to GB47732/64A priority patent/GB1059366A/en
Priority to NO156320A priority patent/NO120103B/no
Priority to DE1965B0080188 priority patent/DE1461066B2/de
Priority to FI650155A priority patent/FI46278C/fi
Priority to NL6500922A priority patent/NL6500922A/xx
Priority to US457753A priority patent/US3286325A/en
Priority to GB18268/66A priority patent/GB1139325A/en
Application granted granted Critical
Publication of US3276102A publication Critical patent/US3276102A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • F16C13/022—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle
    • F16C13/024—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle
    • F16C13/026—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle by fluid pressure
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21F—PAPER-MAKING MACHINES; METHODS OF PRODUCING PAPER THEREON
    • D21F3/00—Press section of machines for making continuous webs of paper
    • D21F3/02—Wet presses
    • D21F3/08—Pressure rolls
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/0006—Driving arrangements
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/02—Rolls; Their bearings
    • D21G1/0206—Controlled deflection rolls
    • D21G1/0213—Controlled deflection rolls with deflection compensation means acting between the roller shell and its supporting member
    • D21G1/022—Controlled deflection rolls with deflection compensation means acting between the roller shell and its supporting member the means using fluid pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19688—Bevel

Definitions

  • the present invention relates to improvements in rolls and particularly to an improved roll structure for obtaining controlled nip pressure between a roll couple.
  • nip pressure is particularly important in papermakin-g machinery, for example, wherein the uniform treatment of a web of paper across its width is essential to obtaining a uniform and satisfactory product, and in a Wet press, for example, uniform extraction of water is dependent upon unifiorm nip load, and in a satisfactory ma chine provisions must be made for varying the overall nip load.
  • An object of the present invention is to provide an improved roll structure which utilizes a cylindrical rol-l shell supported and loaded on its inner surface by a shoe means opposite the nip which is particularly satisfactory in obtaining uniform nip pressures over a range of overall nip loads and is capable of continuous high speed long openating life without rapid Wear and Without requiring frequent part replacement or servicing attention.
  • a further object of the invention is to provide an improved roll assembly capable of controlled deflection for obtaining a uniform nip load which is relatively inexpensive to construct and avoids disadvantages of the structures heretofore available.
  • a still further object of the invention is to provide an improved roll assembly having a roll shell with an inner supporting shoe means wherein superior lubrication is maintained between the shoe means and the shell, and the provision of extensive fluid seals or close manufacturing tolerances is avoided.
  • a still further object of the invention is to provide an improved control deflection roll having an outer roll shell supported on its inner surface opposite its nip area having features which make it particularly satisfactory for use in high speed papermaking machines at the nip loads required and which provides advances over structures heretofore available that make it practical for commercial use in :such environments.
  • the mechanism contemplates providing a ro l] assembly including an outer elongate tubular cylindrical roll shell with a non-rotatable shaft means extending through the shell, means supporting the shaft means, bearing means between the roll shell and shaft means for positioning the roll shell, an elongate limber shoe means having an outer surface co-extensive with the length of the roll shell and being in axially continuous supporting engagement with the inner surface of the roll shell opposite a nip formed with another roll with said surface being rigidly shaped to build up a supporting film of lubricating fluid during relative notation of the roll shell from fluid within the shell, a controlled fluid pressure loading means mounted on the shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that 3,276,102 Patented Oct.
  • FIGURE 1 is a vertical sectional view taken through the axis of a controlled deflect-ion 1 011 constructed and operating in accordance with the principles of the present invention, showing one end of the roll;
  • FIGURE 2 is a vertical sectional view taken substantially on line IIII of FIGURE 1;
  • FIGURE 3 is a smaller sectional view, similar to FIG- URE 1, illustrating the arrangement along the length of the D011;
  • FIGURE 4 is an enlarged detailed fragmentary view showing the end plate at the end of the fluid pressure channel
  • FIGURE 5 is a fragmentary sectional view illustratin the structure of the bearing shoe.
  • FIGURE 6 is a fragmentary side eleuational view of the pivot bar
  • FIGURE 7 is an end elevational view of the pivot bar
  • FIGURE 8 is a fragmentary end elevational view showing an arrangement for two pressure rolls
  • FIGURE 9 is a fragmentary vertical sectional view showing an arrangement whereby the controlled deflection roll is driven
  • FIGURE 10 is a schematic showing of the fluid pressure circuits and control for the controlled deflection roll
  • FIGURE 11 is a graph showing pressure relationships for changing nip pressures and roll deflection.
  • FIGURES 13 show a controlled deflection roll assembly 11 which operates in a roll couple with a second roll in the manner illustrated in FIGURE 8.
  • the roll assembly includes an elongate cylindrical hollow roll shell 12 with a core or inner stationary shaft means 13 extending therethrough.
  • the roll shell 12 is supported opposite the nip by a shoe means 14 which slidingly engages the inner surface of the roll shell 12.
  • the shoe 14 is supported for applying a force to the roll shell by an elongate axially extending piston means or pivot bar 15.
  • the shoe 14 is pivotally supported so as to tiltably conform to the inner surface of the shell 12 and the film of supporting lubricating fluid which builds up between the shoe 14 and inner surface of the shell 12.
  • an elongate pivot pin 16 is positioned between the pivot bar 15 and the shoe 14.
  • the inner non-rotatable shaft 13 has a hollow center 17, being substantially tubular in shape within the roll shell 12, and has radial openings such as 18 for accommodating tubing. At the ends of the shaft are shaft ends 19 which are centrally hollow to accommodate tubing, and bearing lubricating passages 20 extend axially into the shaft ends 19. r
  • the shaft is supported at the ends on self-aligning bearings having parts 21 and 22 and a surrounding support 23 which is suitably mounted in a bracket such as shown in FIGURE 8.
  • the bearing parts 21 and 22. are prevented from rotating relatively to thereby hold the shaft 13 against rotation by a threaded pin 24.
  • the upper controlled deflection roll 11 is supported on a bracket 25 secured to a mounting bracket 26 on a machine frame 27.
  • the controlled deflection roll 11 forms a nip with a lower roll 28 which is suitably supported and may be loaded at its ends by suitable mechanism such as that shown schematically by the arrowed line 29 to control the overall nip pressure.
  • An arrangement of this type provides a press couple for a wet press of a paper machine and while the features of the invention are particularly well adapted to use in paper machinery for presses, calenders and the like it will be appreciated that they may be employed in other environments.
  • bearing rings 30 are bolted to the ends of the roll shell and are supported on bearings 31 on the ends 19 of the shaft. These may be Torrington type bearings secured by a threaded bearing ring 34.
  • Bolted to the bearing ring 35 is an outer ring 32 carrying a sheave 33 for driving the roll shell 12 for finishing the outer surface thereof in preparation for use.
  • the ring 32 has an inwardly extending flange for preventing the escape of lubricant from the bearing 31.
  • the lubricant is supplied through the passage 20 and excess lubricant passes centrifugally out through the passages 35 into the interior of the roll shell and lubricant deflectors 36 bolted to the end of the shaft 13 clear the ends of the oil passages 35 within the shell so that the oil can escape and be returned through the return line as will be later described.
  • the inner surface 37 of the roll shell 12 is smooth and the outer surface 38, FIGURES 2 and is formed to a radius 40 the same as the radius of the inner surface 37 of the shell 12.
  • the leading end of the shoe 14 is removed to provide either a curved or, as shown, a flat surface 39 providing a lubricant collecting wedge shaped area which builds up a film of supporting fluid between the outer surface 38 of the shoe and the inner surface 37 of the shell.
  • the pivotal support of the shoe 14 permits it to accommodate the building up of this supporting layer of fluid and permits the equalization of the pressure of the fluid over the outer surface 38 of the shoe.
  • a shoe 14 with a continuous elongate outer surface 38 which is co-extensive with the length of the shell.
  • a continuous outer surface no concentrations of stress occur and no bending of the shell occurs at unsupported locations. Also there are no nonuniformities along the length of the shell with respect to the generation of heat due to the friction and uniform support is maintained along the entire length of the nip.
  • the shoe 14 is relatively limber so that it can bend with bending of the roll while maintaining a uniform nip pressure and is preferably formed of a chilled casting cold worked 35% before machining.
  • a continuous supporting surface in an axial direction encompasses the surface provided by a one-piece limber beam or by a beam formed in a number of pieces with the pieces closely abutting each other in an axial direction.
  • an axially extending arcuate recess 41 is provided on the inner surface of the shoe, and a similar recess 42, shown in FIGURES 6 and 7, is provided in the pivot bar 15.
  • These recesses 41 and 42 are formed to the radius of the 4 pin 16, which may be in sections along its length. The pivot pin is held at the recesses due to the forces between the pivot bar 15 and the shoe 16.
  • the pivot bar has a recess 43 extending on all surfaces near its base for receiving an O-ring to provide a seal for the liquid in an axially extending channel 44 in which the pivot bar 15 slides.
  • the channel 44 is rectangular in shape and is cut for the full length of the shaft 13.
  • the channel can easily be milled and its ends are closed by end plates 45.
  • end plates are relieved at 45a substantially in line with the surface 49 of the core with the relieved portion preventing the pin 16 from working axially out of the grooves.
  • the end plates are conveniently bolted in place by bolts extending into tapped holes in the shaft.
  • the shaft 13 is formed with a planar surface 49 on each side of the channel 44, and the shoe 14 is wider than the width of the channel 44 so as to have surfaces 48 on each side of the channel which seat on the shaft surface 49 when pressure is relieved from the channel 44, but which clear the surface 49 during normal operation.
  • pressure lines 47 lead to the channel from a main pressure line 47a.
  • the channel is shown as formed in sections with dividers 50 between each of the sections and with the pivot bar 15 similarly formed in sections and the sections abutting the dividers 50.
  • the dividers are conveniently formed by rectangular blocks which are set into the channel and held in place by bolts tapped into the top of the blocks with a sealing material around the edge of the blocks, With this arrangement fluid at different pressures can be directed to the different compartments into which the channel is divided by the dividers 50, although usually for maintaining uniform nip pressure the compartments will be interconnected as shown.
  • Fluid pressure is preferably provided by hydraulic oil delivered from a controlled output pump.
  • a lubricating line 51 For maintaining lubricating fluid such as oil within the inner surface of the shell 12 a lubricating line 51 directs a stream of oil against the inner surface of the shell ahead of the shoe 14. This oil spreads out and provides the built-up layer of lubricating film which forms between the shoe and the shell. Excess oil is returned through an oil return line 52, FIGURES 1 and 3; for aiding in returning the oil, scoops 53 are mounted at the ends of the shaft adjacent the ends of the shoe 14 at the leading edge thereof. These scoops gather up the excess oil that spreads out beyond the end of the shoe and feed it to the return lines 52.
  • lubricating fluid is continually supplied to the inner surface of the shell 12 through the lubricating supply line 51, and a film of lubricating oil builds up in the wedge shaped relieved leading edge 39 of the shoe 14 to build up a supporting film between the outer surface 38 of the shoe and the inner surface 37 of the roll shell 12. Excess oil is returned through the return lines 52.
  • the shoe 14 provides the outer surface 38 which affords continuous support co-extensive with the roll shell 12.
  • FIGURE 9 shows an arrangement for continually driving a roll shell during operation.
  • a roll shell 54 is pro vided with an axially extending annular end extension 57 that is carried in spaced bearings 60.
  • the outer race of the bearings 60 is supported in a self-aligning bearing 61 which accommodates the bending which will occur without stress.
  • the bearings 60 also support the load on the inner shaft 55 supporting the shoe 56.
  • the shaft 55 is supported at its ends on bearings 62a which are carried in the annular extension 57 which is supported by the bearings 60.
  • the extension is also provided with an end 58 to which a drive sheave is secured.
  • FIGURE 10 shows schematically a pressure control ar- 'rangement wherein an initial pressure change is made in the force applied to a roll mounted in fixed bearings, and an automatic change is made to the pressure applied to the inner surface of the roll shell.
  • Forces may be applied to the end of an upper roll 60a by air cylinders 68 at the ends of the roll to control roll bending with air being supplied from an adjustable air pressure valve 62.
  • the valve 62 may be manually operated or may be automatically controlled in response to other operational factors of the machine.
  • the air pressure signal is supplied to a responsive diaphragm 63 which supplies a pressure signal through lines 69 to a diaphragmed pressure balancing chamber 67.
  • the diaphragm of the chamber 67 is connected to a pivotal arm 70 which connects to a diaphragm of a chamber 71.
  • the arm 70 is mounted on an adjustable pivot point and the unit including chamber 67 and 71 is of the type which is available commercially, such as for example, a Hagen ratio totalizer.
  • the pressure signals are referred to by the letter I, with the initial air pressure signal I being supplied at the diaphragm 63, and transmitted through the line 69 to register at I and be converted into a signal I
  • the signal 1 is'supplied to a pressure responsive diaphragm 72 which provides a signal 1,; to control a by-pass valve 73 that regulates the pressure output of an oil pump 74 receiving, oil from a tank 741:.
  • the output of the pump 74 is supplied through an oil pressure line 76 to a chamber 77 operating on a piston beneath at loading shoe 78 within a roll shell 61a.
  • the shell 61a forms a nip N with the upper roll 60.
  • the loaded roll shell is shown below the mating roll 60a and it will be understood that the roll shell may be either above or below the mating roll and is not limited to a particular position.
  • the pressure supplied through the line 76 is shown as I and a pressure indication signal I is fed from the cylinder 77 to the diaphragm within a pressure chamber 64.
  • the diaphragm acts on a lever arm 65 with its pressure signal I to be converted to a pressure signal I by acting on a diaphragm Within a pressure chamber 66, connected to the lever arm 65.
  • the diaphragm is loaded by a spring 90 but the resistance pressure of the spring 90 can be altered by a modifying signal provided from a valve 79 from a constant air pressure line.
  • a modifying signal provided from a valve 79 from a constant air pressure line.
  • FIGURE 11 shows three curves M M and M which result from three different settings of the valve 79.
  • the unit including chambers 64 and 66 can also be a Hagen ratio totalizer or equivalent mechanism.
  • the output signal 1 is supplied to the upper portion of the chamber as signal I
  • the signal I will thus influence the position of the arm 70 and accordingly the pressure transmitted to the channel 77.
  • Changes in the slopes of the pressure relationships M M and M can be varied by changing the location of the pivot point for either the lever arms 65 or 70.
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • a rigid elongate limber shoe means bendable over its length having an outer surface substantially coextensive with the length of the roll shell and being in axially continuous supporting engagement with the inner surface of the shell opposite the nip with said surface being rigid and of substantially the same radius of curvature as the inner surface of the roll shell and having a leading nose surface spaced from and facing the oncoming roll shell inner surface to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load.
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • .bearing means between the roll shell and shaft for positioning the roll shell and to maintain it in alignment With the second roll
  • a shoe means having an outer surface axially substantially coextensive with the roll shell for continuous supporting engagement therewith and having a radial outer surface of substantially the same radius of curvature as the inner surface of the'roll shell and having a leading nose'surface spaced from and facing the oncoming roll shell inner surface to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outw ardly directed forces to said shoe means along the length thereof so that a continuous niploading force is maintained within the roll shell independent of bending of the nip with load.
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • va non-rotatable shaft means extending through said shell
  • bearing means between the roll shell and shaft for positioning the roll shell and to maintain it in alignment with the second roll
  • a shoe means having an outer surface substantially co-extensive with the length of the roll shell and being in axially continuous supporting engagement with the inner surface of the shell opposite the nip,
  • said surface being arcuate and convex and of substantially the same radius of curvature as the inner surface of the roll shell and having a leading nose surface spaced from and facing the oncoming roll shell inner surface for building up a supporting film of lubricating fluid between the roll shell and shoe means from fluid within the roll shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load.
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • bearing means between the roll shell and shaft for positioning the roll shell and to maintain it in alignment with the second roll
  • a shoe means having an outer surface axially substantially co-extensive with the roll shell for continuous supporting engagement therewith and having a rigid radial outer surface of substantially the same radius of curvature as the inner surface of the roll shell and having a leading nose surface spaced from and facing the oncoming roll shell inner surface to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid Within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • a shoe means having an outer surface axially substantially coextensive with the roll shell for continuous supporting engagement therewith and having a rigid radial outer surface of substantially the same radius of curvature as the inner surface of the roll shell and having a leading nose surface spaced from and facing the oncoming roll shell inner surface to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell, a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load,
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • bearing means between the roll shell and shaft for positioning the roll shell and to maintain it in alignment with the second roll
  • a shoe means having an outer surface axially substantially co-extensive with the roll shell for continuous supporting engagement therewith and having a rigid radial outer surface of substantially the same radius of curvature as the inner surface of the roll shell and having a leading nose surface spaced from and facing the oncoming roll shell inner surface to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • bearing means between the roll shell and shaft for positioning the roll shell and to maintain it in alignment with the second roll
  • a shoe means having an outer surface axially substantially co-extensive with the roll shell for continuous supporting engagement therewith and having a radial outer surface rigidly shaped to build up a supporting film of lubricating fluid during relative rotation of the roll s-hell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • said shoe means being circumferentially wider than the channel and resting on said surface with the collapse of pressure in said channel means.
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • a shoe means having an outersurface axially substantially co-extensive with the roll shell for continuous supporting engagement therewith and having a rigid radial outer-surface of substantially the same radius of curvature as the inner surface of the roll shell and having a leading nose surface spaced from and facing the oncoming roll shell inner surface to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe meansalong the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • a roll assembly for forming a pressure nip with a second roll comprising;
  • bearing means between the roll shell and shaft for positioning the roll shell and to maintain it in alignment with the second roll
  • a shoe means having an outer surface axially substantially co-extensive with the roll shell for continuous supporting engagement therewith and-having a rigid radial outer sunface of substantially the same radius of curvature as the inner surface of the roll shell and having a leading nose surface spaced from and facing the oncoming roll shell inner surface to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • a roll assembly vfor forming a pressure nip with a second roll comprising:
  • a shoe means having an outer surface axially substantially co-extensive with the roll shell for continuous supporting engagement therewith and having a radial outer surface rigidly shaped to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • bearing means between the roll shell and shaft for positioning the roll shell and to maintain it in alignment with the second roll
  • a shoe means having an outer surface axially substantially co-extensive with the roll shell for continuous supporting engagement therewith and having a ta 7 dial outer surface rigidly shaped to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying raldially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • a shoe means having an outer surface axially substantially co-extensive with the roll shell for continuous supporting engagement therewith and having a radial outer surface rigidly shaped to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • bearing means between the roll shell and shaft for positioning the roll shell and to maintain it in alignment with the second roll
  • a shoe means having an outer surface axially substantially co-extensive with the roll shell for continuous supporting engagement therewith and having a rigid radial outer surface of substantially the same radius of curvature as the inner surface of the roll shell and having a leading nose surface spaced from and facing the oncoming roll shell inner surface to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • a roll assembly for forming a pressure nip with a second roll comprising:
  • a shoe means having an outer surface axially substantially co-extensive with the roll shell for continuous supporting engagement therewtih and having a rigid radial outer surface of substantially the same radius of curvature as the inner surface of the roll shell and having a leading nose surface spaced from and facing the oncoming roll shell inner surface to build up a supporting film of lubricating fluid during relative rotation of the roll shell from fluid within the shell,
  • a controlled fluid pressure loading means mounted on said shaft means applying radially outwardly directed forces to said shoe means along the length thereof so that a continuous nip loading force is maintained within the roll shell independent of bending of the nip with load
  • each shaft means defining an axially elongate radially outwardly facing continuous channel extending the full length of each shaft means and opening from the ends thereof,

Landscapes

  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Paper (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Knives (AREA)
US339998A 1964-01-24 1964-01-24 Adjustable crown roll Expired - Lifetime US3276102A (en)

Priority Applications (11)

Application Number Priority Date Filing Date Title
FR61716A FR95913E (fr) 1964-01-24 Rouleau a cambrure réglable.
US339998A US3276102A (en) 1964-01-24 1964-01-24 Adjustable crown roll
FR992308A FR1412267A (fr) 1964-01-24 1964-10-22 Rouleau à cambrure réglable
ES0305227A ES305227A1 (es) 1964-01-24 1964-10-23 Perfeccionamientos introducidos en los rodillos para obtener una presion controlada de la linea de sujecion comprendida entre un par de rodillos.
GB47732/64A GB1059366A (en) 1964-01-24 1964-11-24 Adjustable crown roll
NO156320A NO120103B (enrdf_load_stackoverflow) 1964-01-24 1965-01-13
DE1965B0080188 DE1461066B2 (de) 1964-01-24 1965-01-21 Walze fuer die druckbehandlung von papierbahnen
FI650155A FI46278C (fi) 1964-01-24 1965-01-23 Laite säädettävän kuperuuden aikaansaamiseksi onttoihin puristusteloih in.
NL6500922A NL6500922A (enrdf_load_stackoverflow) 1964-01-24 1965-01-25
US457753A US3286325A (en) 1964-01-24 1965-05-21 Support and drive for controlled crown roll
GB18268/66A GB1139325A (en) 1964-01-24 1966-04-26 Support and drive for controlled crown roll

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US339998A US3276102A (en) 1964-01-24 1964-01-24 Adjustable crown roll

Publications (1)

Publication Number Publication Date
US3276102A true US3276102A (en) 1966-10-04

Family

ID=23331466

Family Applications (1)

Application Number Title Priority Date Filing Date
US339998A Expired - Lifetime US3276102A (en) 1964-01-24 1964-01-24 Adjustable crown roll

Country Status (8)

Country Link
US (1) US3276102A (enrdf_load_stackoverflow)
DE (1) DE1461066B2 (enrdf_load_stackoverflow)
ES (1) ES305227A1 (enrdf_load_stackoverflow)
FI (1) FI46278C (enrdf_load_stackoverflow)
FR (1) FR1412267A (enrdf_load_stackoverflow)
GB (1) GB1059366A (enrdf_load_stackoverflow)
NL (1) NL6500922A (enrdf_load_stackoverflow)
NO (1) NO120103B (enrdf_load_stackoverflow)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3418703A (en) * 1966-05-31 1968-12-31 Leon F. Thiry Antideflection roll with non-rotating beam and lever supports
US3419890A (en) * 1965-11-18 1968-12-31 Beloit Corp Crown roll drive
US3521340A (en) * 1968-04-03 1970-07-21 Mount Hope Machinery Ltd Fluid bearing roll with vibration damping means
US3610146A (en) * 1967-05-25 1971-10-05 Victory Kidder Printing Machin Printing machine cylinder mount
US3638292A (en) * 1969-10-29 1972-02-01 Vlaanderen Machine Co Van Roll for applying uniform pressure
US3639956A (en) * 1965-06-25 1972-02-08 Beloit Corp Bearing support and drive for controlled crown roll
US3703862A (en) * 1963-06-25 1972-11-28 Edward Kusters Mas Fab Work pressure rolling assembly
US3766620A (en) * 1972-08-08 1973-10-23 Beloit Corp Controlled deflection roll drive
US3889334A (en) * 1972-08-01 1975-06-17 Beloit Corp Controlled deflection roll drive
US4023480A (en) * 1975-03-04 1977-05-17 Escher Wyss Limited Apparatus for controlling a deflection compensating press roll of a rolling mill
US4192712A (en) * 1977-12-13 1980-03-11 Beloit Corporation Combined breaker size press coater
DE2935630A1 (de) * 1978-09-05 1980-03-20 Beloit Corp Weiterbildung einer feuchtpresse mit erweiterten pressflaechen
US4194446A (en) * 1976-08-20 1980-03-25 Valmet 04 Rolls, such as filled calender rolls, having deflection compensation
US4257844A (en) * 1977-04-15 1981-03-24 Beloit Corporation Press section arrangement
DE3024575A1 (de) * 1980-06-28 1982-01-28 J.M. Voith Gmbh, 7920 Heidenheim Presswalze mit durchbiegungsausgleich
DE3126492A1 (de) * 1981-06-30 1983-01-20 Escher Wyss AG, Zürich "presswalze"
US4414890A (en) * 1980-06-28 1983-11-15 J. M. Voith Gmbh Press roll with adjustable flexion
US20080054212A1 (en) * 2006-08-30 2008-03-06 Honeywell International, Inc. Bearing with fluid flow bypass
CN111074666A (zh) * 2019-09-06 2020-04-28 山东明源智能装备科技有限公司 一种可控中高压光机游泳辊及其变形压力控制系统

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4007522A (en) * 1976-05-26 1977-02-15 Usm Corporation Controlled deflection roll assembly
FI60264C (fi) * 1976-08-20 1981-12-10 Valmet Oy Boejningskompenserad vals laempligen med mjuk yta foer anvaendning i kalander
DE2909277C2 (de) * 1979-03-09 1983-07-21 geb. Pisch Hermengild 4815 Schloß Holte Mitter Walze für die Druckbehandlung von Warenbahnen
DE3329595C2 (de) * 1983-08-16 1993-02-18 Küsters, Eduard, 4150 Krefeld Walze für einen Folienziehkalander
US4679287A (en) * 1984-10-04 1987-07-14 Beloit Corporation Heated variable crown roll
DE3526283A1 (de) * 1985-07-23 1987-02-05 Kleinewefers Gmbh Durchbiegungssteuerbare und beheizbare walze
DE3528333A1 (de) * 1985-08-07 1987-02-19 Kuesters Eduard Walze
DE3533210A1 (de) * 1985-09-18 1987-03-26 Kuesters Eduard Verfahren zur steuerung der liniendruckverteilung in walzenanordnungen und entsprechende steuereinrichtung
JPH0763730B2 (ja) * 1986-04-30 1995-07-12 クレサン 変形可能なケーシングを備える圧延ロール
EP0338235B1 (de) * 1988-04-22 1992-05-06 Eduard Küsters Maschinenfabrik GmbH & Co. KG Dichtungsanordnung
DE3820972A1 (de) * 1988-06-22 1989-12-28 Kuesters Eduard Maschf Walze
DE3843294A1 (de) * 1988-12-22 1990-07-05 Kuesters Eduard Maschf Walzenanordnung mit einer unterwalze mit hydraulischer innenabstuetzung
DE19521859C2 (de) * 1995-06-16 1999-06-24 Kuesters Eduard Maschf Durchbiegungssteuerbare Walze
DE19521860C3 (de) * 1995-06-16 2002-02-28 Kuesters Eduard Maschf Durchbiegungssteuerbare Walze
AT403592B (de) * 1996-02-19 1998-03-25 Andritz Patentverwaltung Saugwalze

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US242058A (en) * 1881-05-24 sohtjrmann
US1868860A (en) * 1927-12-08 1932-07-26 American Bicheroux Company Roller conveyer for glass plates
US2395915A (en) * 1942-07-13 1946-03-05 Harry G Specht Press roll for papermaking
US2854700A (en) * 1952-05-08 1958-10-07 Spinnbau Gmbh Roller equipment
US2960749A (en) * 1958-08-20 1960-11-22 Mount Hope Machinery Ltd Expanding and contracting rolls
US3106153A (en) * 1961-03-09 1963-10-08 Beloit Iron Works Controllable deflection roll
US3119324A (en) * 1960-08-29 1964-01-28 Beloit Iron Works Controlled deflection roll
US3131625A (en) * 1961-06-30 1964-05-05 Kuesters Eduard Maschf Roll for the pressure treatment of web material, especially paper

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US242058A (en) * 1881-05-24 sohtjrmann
US1868860A (en) * 1927-12-08 1932-07-26 American Bicheroux Company Roller conveyer for glass plates
US2395915A (en) * 1942-07-13 1946-03-05 Harry G Specht Press roll for papermaking
US2854700A (en) * 1952-05-08 1958-10-07 Spinnbau Gmbh Roller equipment
US2960749A (en) * 1958-08-20 1960-11-22 Mount Hope Machinery Ltd Expanding and contracting rolls
US3119324A (en) * 1960-08-29 1964-01-28 Beloit Iron Works Controlled deflection roll
US3106153A (en) * 1961-03-09 1963-10-08 Beloit Iron Works Controllable deflection roll
US3131625A (en) * 1961-06-30 1964-05-05 Kuesters Eduard Maschf Roll for the pressure treatment of web material, especially paper

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3703862A (en) * 1963-06-25 1972-11-28 Edward Kusters Mas Fab Work pressure rolling assembly
US3639956A (en) * 1965-06-25 1972-02-08 Beloit Corp Bearing support and drive for controlled crown roll
US3419890A (en) * 1965-11-18 1968-12-31 Beloit Corp Crown roll drive
US3418703A (en) * 1966-05-31 1968-12-31 Leon F. Thiry Antideflection roll with non-rotating beam and lever supports
US3610146A (en) * 1967-05-25 1971-10-05 Victory Kidder Printing Machin Printing machine cylinder mount
US3521340A (en) * 1968-04-03 1970-07-21 Mount Hope Machinery Ltd Fluid bearing roll with vibration damping means
US3638292A (en) * 1969-10-29 1972-02-01 Vlaanderen Machine Co Van Roll for applying uniform pressure
US3889334A (en) * 1972-08-01 1975-06-17 Beloit Corp Controlled deflection roll drive
US3766620A (en) * 1972-08-08 1973-10-23 Beloit Corp Controlled deflection roll drive
US4023480A (en) * 1975-03-04 1977-05-17 Escher Wyss Limited Apparatus for controlling a deflection compensating press roll of a rolling mill
US4194446A (en) * 1976-08-20 1980-03-25 Valmet 04 Rolls, such as filled calender rolls, having deflection compensation
US4257844A (en) * 1977-04-15 1981-03-24 Beloit Corporation Press section arrangement
US4192712A (en) * 1977-12-13 1980-03-11 Beloit Corporation Combined breaker size press coater
DE2935630A1 (de) * 1978-09-05 1980-03-20 Beloit Corp Weiterbildung einer feuchtpresse mit erweiterten pressflaechen
DE3024575A1 (de) * 1980-06-28 1982-01-28 J.M. Voith Gmbh, 7920 Heidenheim Presswalze mit durchbiegungsausgleich
US4414890A (en) * 1980-06-28 1983-11-15 J. M. Voith Gmbh Press roll with adjustable flexion
USRE32586E (en) * 1980-06-28 1988-02-02 J. M. Voith Gmbh Press roll with adjustable flexion
DE3126492A1 (de) * 1981-06-30 1983-01-20 Escher Wyss AG, Zürich "presswalze"
US20080054212A1 (en) * 2006-08-30 2008-03-06 Honeywell International, Inc. Bearing with fluid flow bypass
US7789567B2 (en) * 2006-08-30 2010-09-07 Honeywell International Inc. Bearing with fluid flow bypass
CN111074666A (zh) * 2019-09-06 2020-04-28 山东明源智能装备科技有限公司 一种可控中高压光机游泳辊及其变形压力控制系统

Also Published As

Publication number Publication date
FI46278C (fi) 1973-02-12
FI46278B (enrdf_load_stackoverflow) 1972-10-31
ES305227A1 (es) 1965-03-16
NO120103B (enrdf_load_stackoverflow) 1970-08-24
DE1461066B2 (de) 1976-10-28
FR1412267A (fr) 1965-09-24
DE1461066A1 (de) 1968-12-12
GB1059366A (en) 1967-02-22
NL6500922A (enrdf_load_stackoverflow) 1965-07-26

Similar Documents

Publication Publication Date Title
US3276102A (en) Adjustable crown roll
US4796452A (en) Setting device for adjusting the position of a roll
EP0527881B1 (en) Press roll
US4414890A (en) Press roll with adjustable flexion
US4287021A (en) Extended nip press
USRE30268E (en) Hydrodynamically loaded web press with slipper bearing shoes
EP0365523B1 (en) Self-loading controlled deflection roll
US3766620A (en) Controlled deflection roll drive
US3889334A (en) Controlled deflection roll drive
CA2147730A1 (en) Roll for a papermaking machine
EP0897484B1 (en) Hydrostatic glide bearing for a roll or equivalent
US3362055A (en) Hydraulic anti-deflection roll
US4899656A (en) Machine for processing a continuous web or sheets
US5189776A (en) Roller
EP1127187A1 (en) A press for the dewatering of a fibre web
CA1307967C (en) Press rolls
FI82394C (fi) Kombinerat hydrostatiskt/hydrodynamiskt lagersystem foer kvarnapparat.
FI68886C (fi) Pressvals med en anordning foer korrigering av valsmantelns neboejning
USRE31923E (en) Extended nip press
US4856155A (en) Method and device in an adjustable-crown roll
EP0107607A2 (en) Extended nip press
US3418703A (en) Antideflection roll with non-rotating beam and lever supports
US4308651A (en) Controlled variable deflection roll
GB2024990A (en) Controlled deflection rolls
US5984847A (en) Self loading controlled deflection roll